Target throwing apparatus having automatically varied throwing angle



Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWXNG APPARATUS HAVING AUTOMATICALLY VARIED THRQWING ANGLE Original Filed June 12, 1958 13 Sheets-Sheet 1 FIG. I

34 FIG. 2 3a 4420 a a 5 33 so' 5, 35 I26 175 m 448 L l. I! Q 4a 149 (IS-] G V I47 |4s INVENTOR. HARRY CLARK FOSTER HIS ATTORNEYS Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12, 1958 13 Sheets-Sheet 2 IN VEN TOR.

m '5 HARRY CLARK FOSTER HIS ATTORNE Y5 Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12, 1958 15 Sheets-Sheet 5 FIG. 4

INVENTOR.

HARRY CLARK FOSTER {iii/w" HIS ATTORNEYS Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12, 1958 15 Sheets-Sheet 4 FIG. 5

INVENTOR.

HARRY CLARK FOSTER HIS ATTORNEY Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12, 1958 13 Sheets-Sheet 5 INVENTOR.

HARRY 0 LARK FOSTER HIS ATTORNEY Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY 13 Sheets-Sheet 6 VARIED THROWING ANGLE Original Filed June 12, 1958 FIGJBR 293 I I I I I I, i i: 121::

, fi J FIG. 7

INVENTOR.

HARRY CLARK FOSTER HIS ATTORNEY Dec. 28, 1965 H. c. FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12, 1958 13 Sheets-Sheet 7 INVENTOR.

HARRY CLARK FOSTER H15 ATTORNEY H. c. FOSTER 3,225,754 TARGET THHOWING APPARATUS HAVING AUTOMATICALLY Dec. 28, 1965 VARIED THROWING ANGLE l5 Sheets-Sheet 8 Original Filed June 12, 1958 INVENTOR.

HARRY CLARK FOSTER HIS ATTORNEYS Dec. 28, 1965 H. c. FOSTER 3,

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12; 1958 13 Sheets-Sheet 9 CIRCULAR HUB I70 PIVOTED OF'F- CENTER INVENTOR.

HARRY CLARK FOSTER HIS ATTORNEY H. C. FOSTER Dec. 28, 1965 TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE l3 Sheets-Sheet 10 Original Filed June 12, 1958 9 com 3 INVENTOR.

HARRY CLARK FOSTER 8W 5 W HIS ATTORNEYS Dec. 28, 1965 H c FOSTER 3,225,754

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE l3 Sheets-Sheet 11 Original Filed June 12. 1958 INVENTOR.

m& T. S o F 5 K H M N L M C T T Y. R A R 5 A H H Y B Dec. 28, 1965 H. c. FOSTER 3,

TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Original Filed June 12, 1958 15 Sheets-Sheet 12 FIG. I5

248 m BIO 315 27/ 3|? V E- /304 i 305 303 L- INVENTOR.

HARRY CLARK FOSTER HIS ATTORNEYS Dec. 28, 1965 VARIED THROWING ANGLE Original Filed June 12, 1958 13 Sheets-Sheet 15 wO2OUmm 2- MEE- mm vm mm mm N mDZOUmm Z ME; Q m

O'Bld INVENTOR.

HARRY CLARK FOSTER HIS ATTORNEYS PIG;-

United States Patent 3,225,754 TARGET THROWING APPARATUS HAVING AUTOMATICALLY VARIED THROWING ANGLE Harry Clark Foster, East Alton, Ill., assignor to Olin Mathieson Chemical Corporation, East Alton, 111., a corporation of Virginia Original application June 12, 1958, Ser. No. 741,571, now Patent No. 3,119,383, dated Jan. 28, 1964. Divided and this application Aug. 15, 1960, Ser. No. 61,795

8 Claims. (Cl. 1249) This invention relates to target traps such as are used for throwing targets known as clap pigeons and more particularly to power driven traps wherein targets are automatically fed from a magazine to a throwing arm and said trap is adapted to vary automatically the angle at which the targets are thrown. This application is a division of copending application Serial No. 741,571, filed June 12, 1958 and since matured into Patent No. 3,119,- 383.

In the art of shooting targets of the clay pigeon type, it is desirable that the shooter be unable to anticipate direction of flight of successive targets. Heretofore some traps designed to prevent such anticipation by the shooter by throwing targets at random angles, have employed chance wheels for the purpose While others have depended upon the random motion of certain of the trap elements. Utilization of power operation, from the same source, instead of manual operation with such traps complicates the mechanism necessary to operate both the throwing and angling mechanism. For example, in such traps the throwing arm is usually operated by a strong spring which must be cocked or energized prior to the firing time and the power requirement for this purpose is thus intermittent. Prior devices have heretofore either operated the electric motor intermittently and automatically in operating the cocking mechanism and the angle changing mechanism, which is unsatisfactory, among other things, from the standpoint that the motor must on each cocking stroke and angle changing movement start under a dead load with the attending heavy wear. Prior devices have in the alternative utilized complicated clutches and the like to connect a continuously running motor to both the cocking and the angle changing mechanisms.

In addition, all of these prior art devices are such to the effect that the distribution of targets over the flight zone is not or cannot be balanced evenly. As a consequence, some of these shooters will have an advantage over others in that the former will have more targets concentrated in a given section of the flight zone or the latter may have targets distributed widely over the entire flight zone. This condition not only results in an unequal testing of the skill of respective shooters, but is a source of great dissatisfaction among shooters generally. Uniform distribution of targets over the whole of the flight zone in directions unpredictable for respective targets by the shooters would be the most desirable combination for the game of trap shooting. Prior devices have failed to provide this combination, by depending for direction change upon a certain repetitive cycle of uniform motion which has the defect that an experienced marksman working with a given trap is often able with little effort to learn the sequence of direction peculiar to that trap. This enables him to predict with some degree of certainty the direction in which the nexttarget is to be launched, affording him thereby an advantage over competitors. It is therefore an object of this invention to provide a target trap with means for varying the direction of throw such that this variation takes place in a cycle of unpredictable, non-uniform motion.

Another object is to provide an improved trap containing novel means for continually varying the angles at which the targets are discharged in a continuous and repetitive cycle of non-uniform motion.

Another object is to provide an improved means for continuously changing the angles at which the targets are launched.

Still another object of this invention is to provide an improved trap containing novel continuous means for varying the direction of throw such that this variation involves the selection of flight of successive targets with a maximum variety over substantially the entire flight zone in a balanced but not readily predictable sequence.

A further object of this invention is to provide an improved target trap with novel continuous means for establishing a series of target launching directions in a thoroughly mixed sequence which is exceedingly difficult to predict and equally difiicult to follow over a substantial period of operation of the trap.

Another object is to provide a target trap of simple and rugged construction with a minimum of parts to effect an automatically and continuously varied throwing angle.

Other objects and advantages of this invention will be apparent from the following description .and drawings in which:

FIGURE 1 is a side elevation view of a preferred embodiment of the invention taken at the moment immediately after a target has been thrown;

FIGURE 2 is a plan view of the embodiment of FIG- URE 1;

FIGURE 3 is a fragmentary cross-sectional view in elevation taken on line IIIIII of FIGURE 2.

FIGURE 4 is a fragmentary cross-sectional view taken on line IVIV of FIGURE 3, illustrating certain details of the holding, cocking, transmission and release mechanism involved;

FIGURE 5 is a fragmentary cross-sectional view taken along the lines VV of FIGURE 4;

FIGURE 6 is a fragmentary cross-sectional view taken along line VIVI of FIGURE 4;

FIGURE 7 is a partial plan view of the throwing arm in the cocked position in the embodiment shown in FIGURE 1 in cocked relation to the target feed shelf;

FIGURE 8 is an elevational fragmentary view partly in cross-section taken along line VIIIVIII of FIGURE 7 and also showing the target escapement mechanism;

FIGURE 9 is a plan view of the base in the embodiment shown in FIGURE 1;

FIGURE 10 is an expanded elevational view developed- -along the line X-X of FIGURE 9;

FIGURE 11 is a cross-sectional view taken along the line XIXI of FIGURE 10;

FIGURE 12 is a cross-sectional view taken along the line XIIXII of FIGURE 10;

FIGURE 13 is a cross-sectional bottom view taken along line XIII-XIII of FIGURE 3;

FIGURE 14 is a cross-sectional view of the release mechanism of the magazine taken along line XIV-XIV depicted in the embodiment shown in FIGURE 1;

FIGURE 15 is a diagrammatic view of the electric power and control system employed with the embodiment illustrated in FIGURE 1;

FIGURE 16 is a time and motion diagram showing the distribution of targets, by the angle changing mechanism across the shooting field with respect to time interval;

FIGURE 17 is a partial side view on line XVIIXVII of FIGURE 7; and

FIGURE 18 is a partial bottom view on line XVIII-XVIII of FIGURE 17.

In accordance with this invention, there is provided a trap powered by a continuously running motor which engages the trap mechanism through a clutch system to cock a spring which upon being released rotates the target throwing arm mounted upon a rotatable shaft located in the clutch system, to effect throwing of the target which is then followed by automatic loading of another target to the throwing arm as the result of continued movement of the mechanism. The loading of targets is facilitated by means of a rotary magazine containing a plurality of targets in annular arrangement in said magazine which is indexed by the rotation of the aforesaid shaft through a linkage arrangement interconnecting the magazine and the shaft. The sequence of target throwing, cocking of the mainspring of the trap, indexing of the magazine and reloading of the target throwing arm occurs substantially automatically in the apparatus upon release of the target throwing arm by the operator.

A second motor is provided which engages a novel gear arrangement which creates and transmits a nonuniform motion embodying intermittent acceleration, deceleration, reversing and hesitating motions to the target trap thereby continuously and independently oscillating the target trap in order to vary the distribution of the released targets.

The apparatus of this invention may be described generally as comprising a base 145, a sub-base 144, a frame support 143, a gear housing 3, a mainspring housing 4, a target carrier or throwing arm 5, a mainspring 6, an electric motor 7 which supplies power for cocking the trap, a magazine support housing 1, a frame 2, and an electric motor 248 supplying power for the self angling mechanism. Frame 2, and housing 1, 3, and 4, are fixed together by any suitable fastening means so as to constitute in effect a single frame. Base 145 contains the angle changing mechanism and has mounted on it sub-base 144. Frame support 143 is rotatably mounted on sub-base 144 and supports the composite frame described above. Power is supplied by the continuously operating motor 7 to the cocking mechanism and the holding mechanism, releasing mechanism, and sprocket 142 of the indexing mechanism, which mechanisms are contained in gear housing 3. The target carrier or throwing arm 5 is mounted for rotation upon the upper end of a shaft 8 to which is imparted a rotational thrust for throwing the target by means of the mainspring 6 disposed protectively under the mainspring housing 4. A rotatable magazine assembly 257 is detachably mounted on housing 1 and through appropriate mechanism is indexed by power supplied through the rotation of shaft 8.

The cocking, holding, releasing, target loading mechanisms and the driver for the indexing mechanism are a compact unit, generally indicated as 24 in FIGURE 3, contained in and associated with gear housing 3. The motor continuously turns one gear of an epicyclic gear train in the gear housing 3 while the rest of the train may be set into operation to cock the throwing arm intermittently following each throwing operation. Upon actuation of the release mechanism the cocking mechanism is adapted to transmit power from the motor 7 through the entire gear train at a suitable speed reduction through the main shaft 8 to the mainspring 6 and through sprocket 142, mounted on the mainshaft, by appropriate linkages to the rotary magazine. The gear train rotates the main shaft 8 to tension the mainspring 6 until the mainspring crank 9 attached to the lower end of shaft 8 is beyond the out dead center after which the shaft 8 and carrier arm 5 are turned ahead some further distance, without shock, to the cocked position whereupon the target carrier is held cocked and the gearing is again set to idle. The rotation of main shaft 8, in addition, during cocking rotates an escapement cam 194 by means of an appropriate linkage from sprocket 142 to release a target for transfer to a target feed shelf 126. As the target carrier proceeds to the cocked position, a

target is then automatically fed to the carrier plate 33 ready for launching. The target is thrown when the release mechanism is actuated electrically from a remote position. In a travel of the throwing arm 5 from the cocked to the firing position the main shaft 8 traverses the same angle as the aforesaid arm thereby rotating sprocket 142 through a corresponding angle which activates by appropriate linking means the indexing mechanisms for the rotary target carrier.

In order that the elevation at which the targets are ejected may be controlled, there is provided an elevation adjustment screw 10 mounted rotatably but not slidably on housing 4 and passing threadedly through a swivel 11 pivotally carried by the upright 255 of frame support 143 and the other end of which is provided with a crank handle 13.

The second motor 248 mounted independently of the target throwing apparatus drives, by means of an appropriate gear train, a gear 170 mounted on shaft 171 at a constant rate. In accordance with this invention, a hub 172 is mounted eccentrically at the center of gear 170 and in turn, the hub, has mounted rotatably about it a second gear 177. Movement of gear 177 is controlled by means of an anchoring link 178 pivotally mounted to gear 177, which limits the movement of this second gear about the hub to an accelerating, decelerating, hesitating and reversing motion. This motion is transmitted to a ring gear 179 which by a second link 148 transmits this motion to the frame for the desired oscillation of the trap.

Main shaft 8 through sprockets 112 and 142, link chain and a Geneva gear assembly, comprising an indexing arm 109, an indexing gear 15, transmit through drive shaft 200 and other appropriate gearing, an indexing rotary movement to the target carrier. This indexing movement imparts to the carrier, step by step, a rotary motion, bringing successive stacks of targets into register with feed shelf 126 to which a target is transferred by appropriate means. Mounted fixedly to the indexing member 15 and sprocket 112 is an escapement cam 194 with a protuberant surface 280 and a receding surface 281 operating a follower which controls the discharge of targets from the bottom; of each successive stack when in register with the feed shelf 126.

The invention will be better understood from the following more detailed description with reference to the embodiment of the invention illustrated in the drawing.

As is shown most clearly in FIGURES 1 and 9, the entire trap is mounted upon a base which is provided with means such as holes 249, 250 and 263 for attaohing the base to any suitable support, and upon which is pivotally mounted a sub-base 144. Fixed about the periphery of sub-base 144, and in base 145, are a series of windage adjustment holes 252 for correction of and fixing the target assembly against variation of wind direction and velocity. Extending from and integral with sub-base 144 is an adjustment arm 242 having mounted on it a bracket 251 and containing a hole 253 in circumferential alignment with holes 252. A plunger 285 with notch 245 and enlarged head 286 is placed in slidable relationship in hole 253 for engagement with holes 252. Head 286 serves as a base for spring 287 which forces and maintains a plunger head 286 into a hole 252. Pivotally mounted on bracket 251, by means of pin 244, is a release lever 243 having an end 246 in engagement within notch 245.

Pivotallly mounted on sub-base 144 by means of a hearing assembly 254 is a swivel base 143 which is provided with upright supports 255.

The bearing assembly is constructed of multiple bearings mounted within outer race 186 and an inner race sub-assembly consisting of elements 187, 188 and 189. Outer race 186 is fixed, by means of a plurality of screws 191, to swivel base 143. The inner race subassembly consists of a lower race 188 and an upper race 187 sandwiching between them, for appropriate adjustment of the assembly, a number of shims 189. This subassembly is fixed to sub-base 144 by bolts 256.

Mounted pivotally on upright supports 255 is the frame housing 2 by means of elevation pivot shaft 17 which passes through the upper part of the uprights 255. Frame 2 carries motor 7, the gear housing 3 and also the magazine support housing 1. Integral with the upper part of support housing 1 are magazine supports 216 into which is inserted suitable means such as pins 217 for attaching a magazine assembly 257. Attached to the front of the gear housing 3 is the mainspring housing or apron 4 which protectively covers and also provides a mount for one end of the mainspring 6 which provides the sudden thrust of throwing power needed to project a target in desirable fashion. The other end of the mainspring 6 is attached to the mainspring crank 9 which in turn imparts a rotational thrust to the main shaft 8 passing through the gear housing 3 and journaled at its lower end in the bottom of housing 3. The upper end of main shaft 8 is indirectly journaled through the hub 27 of feed cam 31 in the gear housing cover 29 fromwhich the shaft protrudes sufiiciently to carry the carrier or throwing arm 5 with its other components by means of a splined fitting 32 at the upper end of the shaft 8. The arm and cam are retained on shaft 8 by spring 258 and nut 259 by means of screw threads also at the upper end of shaft 8.

The target carrier or throwing arm 5 has a carrier plate 33 and a rubber or other resilient material faced rail 34. The arm 5 is formed with an upward tilt of about 5 as an extension of the circular hub portion 35- which is provided with an opening 37 internally splined at 36 for attachment to the splined fitting 32 of the main shaft 8. At the outer end of arm 5 and supported underneath it is a carrier plate 33 which supports the target in its initial travel during the throwing operation from the moment of firing to the moment when the target leaves the arm. Although plate 33 in this embodiment is attached to arm 5, it is to be understood that plate 33 could be a separate stationary member mounted on frame 2 and of suitable arcuate length to support the target while it is propelled by the rail 34. In this embodiment described, the leading edge of the plate 33 adjacent shelf 126 in cocked position is formed with a projection 175 to prevent interference with the trailing edge of the target in throwing. Depending from the carrier arm 5 is the angularly adjustable rail 34, having attached to it by means of fasteners 260, the resilient ieading edge 38, and which is pivotally attached at the inner end to arm 5 at the fastener 39 to extend outwardly above the carrier plate 33 at least to the slot 40. Angular control of the target trajectory and control of the levelness of the trajectory is attained by angular movement of the adjustable carrier rail 34 about pivot 39 to a desired position of the outer carrier rail support 41 as determined by the position of support fastener 42 in the arcuate slot 48 in the carrier plate 33. Slot 40 is of such length as to permit the rail 34 to be adjusted to an angle of lead or lag as necessary to correct for the effect of windage on ievelness and direction. For example, a lagging rail causes a target discharge to the right with a tendency to a right tilt, whereas a leading rail causes a target discharge to the left with a tendency to a left tilt. Toreduce the moment of inertia, the arm 5 is cast of a light metal such as a suitable magnesium alloy or the like and the light metal carrier plate 33, it will be noted from FIGURES 2 and 7 in particular, has a number of openings or cut out sections. It is to be noted that the rail 34 is adapted to be reversibly mounted to compensate for wear.

The main power for throwing the target with the sudden acceleration necessary is supplied at the lower end of the main shaft 8 by mainspring 6, the ends of which are threadedly secured to an adjustable internally threaded mainspring plug 43 at the front end and similarly to a second mainspring plug 44 at the rear for connection to the mainspring crank 9 as shown in FIGURE 3. The rear mainspring plug 44 is pivoted at one end to the crank 9 by means of mainspring crank stud 45 which is rotatable in crank stud bushing 46. The other or front mainspring plug 43 threadedly receives the T- hcaded mainspring adjusting screw 47 which in turn passes through mainspring swivel block 48 and through a slotted opening 49 in the frame 4. Screw 47 permits adjustment of the mainspring tension. The swivel block 48 permits lateral oscillation of the mainspring 6 without bending the spring. Mainspring 6 is a closely coiled spring. However, in order to permit a relatively heavy spring to be utilized in a longitudinally small space of length mainspring 6 may be a closely wound fiat metal ribbon coiled edgewise.

The mainspring crank 9 is fixedly attached at its hub to the lower end of the main shaft 8 by means of a key 50 and a clamp screw 51. The main shaft 8, as is shown in FIGURE 4, extends through the bottom of the gear housing 3 and is there rotatably supported in a main shaft lower bearing 52. Also fixedly mounted by means of key 261 at the lower end of main shaft 8 and between the main shaft 8 and the housing 3 to prevent loss of the oil bath contained in the housing. Upon expenditure of the throwing power stored up in the spring 6 at the conclusion of a target throwing operation, cocking power is automatically channeled from the continuously operating motor '7 through the flexible coupling 262 (FIGURES 3 and 13) and the worm drive shaft 55 to the epicyclic gear train in gear housing 3 by way of the worm gear wheel 56 (FIGURE 5).

In the gear housing 3, worm drive shaft 55 having a worm 55A of sufficiently steep lead to avoid self-locking, is journaled in worm shaft bushings 57 and 58 (FIGURE 5). The worm gear wheel 56 and also the firing ratchet 59 are mounted fixedly by means of key 60 on the hub 61 of the sun gear 62. The hub 61 in turn is rotatably mounted by means of sun gear bushings 63 and 64 on the main shaft 8. Also located in housing 3 is the control cam 65 fixedly mounted by means of the lower splined fitting 66 on the rotatable main shaft 8. Carried 0n the control cam 65 are the planet studs 67, 68 and 69. Mounted rotatably on a shoulder of the control cam 65 is the internal ring gear 73 with the external ratchet 74. The planet gears 70, 71 and 72 are also in engagement with the sun gear 62 and the ring gear 73. Control cam 65 is provided at its lower end with a cam surface having a protuberant control portion cam surface 75 and a reeessed control cam surface 76 generated by a shorter radius than that which generates the protuberant portion 75.

Control cam 65 also has a rim portion 77 in which is formed a holding notch 78 designed for coaction with a sear 79 formed on the lower portion of the sear member 80 which is rotatably carried by shaft 81 journaled in gear housing 3. The upper end of the sear member 80 is provided with an operating arm 82 linked by means of the firing bar stud 83 to one end of firing bar 84 adjacent to the other end of which, resting in slotted end of guide 114, there is provided a firing pawl shoulder or abutment 85 and a control extension 174. This end of the firing bar is adapted to be acted upon by the firing pin 113 slidably carried in firing pin guide 114 mounted on housing 3 under the impetus of plunger 86 of the release solenoid 87 so as to force pawl shoulders 85 into the teeth of the ratchet wheel 59. Extension 174 is a release solenoid 8-7 so as to force pawl shoulder 85 into wheel 59 and thus determines the extent of movement of bar 84. Pressing against the other end of firing bar 84 adjacent the stud 83 and tending to turn the bar 84 about stud 83 counter-clockwise (FIGURE 5) against plunger 86, is the sear plunger 88 which is yieldably mounted against the sear spring 89 carried in an extension of the housing 3 known as a sear plunger bushing 247. Sear plunger 88 also functions througth firing bar stud 83 to turn operating lever 82 clockwise so as to urge sear 79 into notch 78.

In order to reduce the weight and moment of inertia. of the parts of the trap which turn in unison during the throwing operation so as to obtain the highest proportion of target throwing spring power, it will be noted (FIG- URE 4) that the control cam 65 is almost entirely hollowed out except for three radial ribs each of which carries one of the planetary gears and connects the rim and cam portions of cam 65 to its hub portion. To further reduce its weight, the cam 65 may consist of a suitable light meal or alloy.

Also mounted in housing 3 is a cocking pawl 91 the hub 92 of which is pivotally mounted on the eccentric hub 93 of the hold back pawl 94 which in turn is pivotally mounted on and carried by the shaft 95. The upper end of the cocking pawl 91 is provided with a tooth 96 for engagement with the teeth or serrations of the external ratchet 74 carried on the ring gear 73.

When the tooth 96 of pawl 91 engages with the ratchet 74, the force of ring gear 73 on the cocking pawl 91 acting through the eccentric hub turns the hold back pawl 94 clockwise into engagement with the ratchet 74 (FIG- URE 6). The lower end of cocking pawl 91 carries a follower 97 for engagement with the cam surfaces 75 and 76 of the control cam 65. One side of the end of hold back pawl 94 is also adaptable for engagement with the: teeth or serrations of the ratchet 74 of the ring gear 73. Bearing against the back side of the cocking pawl is the cocking pawl spring 98, acting to thrust the cooking pawl. 91 away from the wall of the gear housing into or toward both the ring gear 73 and control cam 65. The other side of the end of hold back pawl 94 is formed to act as an armature seating against a pawl holding permanent magnet 99, which is mounted on a non-magnetic member 101 carried by and extending into housing 3. Magnet 99 is fastened to member 101 by means of a U- shaped strap 100 having limited pivotal movement to aid both poles of magnet 99 to seat on pawl 94. However, the magnet may be rigidly mounted. The structure of the cocking pawl 91 and the hold back pawl 94 is such that in cooperation with the gearing these members prevent undesired acceleration and the shock movement which would result after the mainspring crank stud 45 has passed the out dead center at the conclusion of the cocking operation.

To permit manual operation of the trap for testing or the like, gear housing 3 also contains a trigger dog 102 pivotally mounted by means of trigger arm shaft 103 on gear housing cover 29 and adapted to be turned against the operating arm 82 of the sear member 80 (FIGURE when the handle of the trigger 105 is pulled up (FIGURE 1). Trigger 105 mounted pivotally outside frame 1 acting through the trigger pull rod 106 and the trigger arm 107 is disposed above gear housing cover 29 and is attached to the upper end of trigger arm shaft 103 to the lower end of which dog 102 is attached and causes the dog 102 to turn counter-clockwise (FIGURE 5) to press against operating arm 82 turning the sear member 80 and its sear 79 counterclockwise so -as to lift sear 79 out of the notch 78 in the rim of control cam 65 (FIGURE 6).

Suitably secured on gear housing 3 is a cover 29 in which hub 27 of target feed cam 31, mounted on main shaft 8, is rotatably mounted by means of an upper main bearing 108 (FIGURE 4). Separation of cover 29 and cam 31 is prevented by a feed cam collar 104 secured on the end of the hub 27 of cam 31 by means of feed cam collar pins 104a. Target feed cam 31 has a well for receiving the hub of carrier arm 5 so as to permit a greater degree of engagement between arm 5 and main shaft 8 at the splined fitting 32.

Fixedly secured against rotation by means of pin 282 in the lower and forward part of magazine support housing 1 is a shaft 54 having formed at its lower end a head 283. Rotatably mounted on shaft 54 by means of bushing 284 are escapement cam 194 sprocket 112 and indexing disc 15. Cam 194, sprocket 112 and disc 15 are fixedly assembled to each other by means of pins 21 so that they rotate as a unit about shaft 54. Escapement cam 194 is provided about its periphery with a cam surface having a protuberant control portion 280 and a recessed clearance surface 281 generated by a shorter radius than that which generates the protuberant portion 280. The protuberant portion 280 of escapement cam 194 extends through an angle of about and the receding portion traverses an angle of 250.

Disc 15 has a concentric lateral surface 20 extending through an arc of about 270 and of a radius to have a sliding fit within the locking surface 18 of indexing gear 14 described below. The disc has through an arc of a concave clearance 28 which is formed on a radius to permit free movement of the indexing gear 14 through said clearance 28. Extending from and integral with this disc 15 is an arm 109 having mounted on its end by means of pin 110 an indexing drive roll 12. The diameter of roller 12 is such as will permit its engagement within slots 16.

Extending through the magazine support housing 1 is an escapement shaft 198 rotatably supported by bushings 268 and 269. Fixedly mounted at the upper end of shaft 198 by means of pin 295 is an escape-ment lever 270 from which extends an arm 199. Fixedly mounted on the lower end of shaft 198 is the escapement driver arm 196 having mounted on its free end by means of pin 197 an escapement follower 195 which rides in engagement on control surfaces 280 and 281 of cam 194.

An indexing shaft 200 extends through the rear of magazine support housing 1 and is mounted thereon at its lower end by means of bushing 266 and at its upper end by means of bushing 267. Fixedly mounted on the upper end of shaft 200, by means of pin 271, is a gear 215. Fixedly mounted on the lower end of shaft 200, by means of pin 201, is an indexing gear 14. Gear 14 has four equally spaced driving slots 16 and intermediate equally spaced locking surfaces 18.

Power to operate the aforedescribed driving disc 15, escapement cam 194, and driving gear 14 is transmitted to sprocket 112 by means of a linking drive chain 115 connecting said sprocket to sprocket 142 mounted about main shaft 8.

Mounted above magazine support housing .1 and in supports 216, by means of support pins 217, is a maga- Zine assembly hereinafter described. The magazine assembly consists of a circular base 202 containing a network of raised reinforcing members 207, 207A, 208, 210, and 228 variously extending from hubs 227, 227A, 229 and pad 211. Base 202 has mounted to it and extending from it by means of fasteners 265 an annular ring portion 218 completing the base structure. Rib 228 defines an area which encompasse escapement lever 270 and hub 220. Annular ring 218 contains an aperture 219 which defines the opening for a target from a plurality of stacks supported above the base. Slidably mounted in bosses 205 and 206 is an escapement rod 203 of which one end abuts escapement arm 199 against which it is held by means of spring 214 acting on the other end. Spring 214 is fixedly mounted on base 202 by means of a holder assembly. Spring holder assembly consists of pad 211 and plate 212 which sandwich fixedly between them the spring 214 by means of bolts 213.

Pivotally mounted at 232 by means of a pin 234 on magazine spider 23 about and above opening 219, is shown a tar-get escapement assembly 235 having three protruding arms 236, 237 and 238. Pivotally mounted at the end of arm 238 by means of screw 233 is a resilient cushion 241 for engagement with either the bottom or second to bottom target during the operation of the trap. Holding the resilient cushion 241 for engagement with the targets is a spring 271 mounted at one end by mean of hole 272 to arm 237 and at its other end to magazine outer guide rail 230.

Suspended below annular plate 218 is a single bracket 164 having mounted within it by means of pin 163 a target fee-d finger 162 which is yieldably held in position by gravity.

Rotat-ably mounted about the magazine base is a magazine spider 23 mounted on stud 223 having a headed end 275 and which itself passes through bushing 278, and has a shoulder portion resting on thrust washer 276 and a reduced body portion 277 which mounts the spider rotatable to base 202, to which it is secured by means of lock washer 279 and nut 224. The interior structure of magazine spider 23 contains a hub 274 about which is mounted fixedly by means of key 225 a gear 226 which meshes with gear 215 mounted on magazine drive shaft 200. The ratio of gear 226 to gear 215 i such as will bring each of the stacks of targets, mounted in the magazine successively in register with opening 219 in the base of the magazine. In the instant embodiment wherein 10 stacks of targets are employed this ratio is 2.5 :1. Mounted on spider 23 are guide rails 230 and 231. These three guide rails define the magazine space for holding a stack of nested targets. At the lower end, rails 230 extend below the lower end of rail 231 to below annular ring 218. The lower end of guide rail 231 extends to just above escapement cushion 241 to permit free movement of the resilient cushion mounted on arm 238 of assembly 235 and serves as a stop limiting clockwise rotation of escapement assembly 235.

Mounted on the feed shelf operating bracket 125 below the magazine is a target feed shelf 126 which coacts with the target feed arm 127 one end of which is pivoted on the gear housing cover 29 and carries rotatably intermediate the ends of arm 127 a feed cam roll 128 mounted on arm 127 by means of stud 129 and bushing 140 (FIGURE 4) which follows the profile of the target feed cam 31 and thereby controls the operation of the target feed shelf by means of feed shelf roll 161. Depending from and attached to bracket 125 are a pair of spaced feed shelf guide rods 130 and 131 which slidably engage with feed shelf guide bushings 132 and 133 which are mounted on and protrude from the upper surface of frame 2 at the feed shelf. Disposed about each bushing and guide rod is a feed shelf lifting spring such a springs 134 and 135 mounted in compression between bracket 12-5 and frame 2. Accurate positioning of the feed shelf 126 is obtained by interpositon of feed shelf shims 136 between the shelf 126 and the bracket 125. It is evident that the feed shelf 126 is raised by feed shelf lifting springs 134 and 135 and is lowered by target feed cam 31 in timed relationship with the rotation of carrier arm 5.

Depending and protruding below feed shelf 126 is a guide 289 into which is mounted a target guide button 169. Guide 289 has at its lower end a slot 292 and a groove 291. Fixedly attached to the lower end of button 169 and perpendicular to its cylindrical axis is a cross-member 293 which in normal use is engaged in slot 292. Disposed about button 169 is a lifting spring 290 which maintains cross-member 293 in slot 292 and forces button 169 to protrude above feed shelf 126 (FIGURES 17 and 18). In the use of the trap for doubles, button 169 is pushed in against spring 290' until cross-member 293 is below guide 289 and out of engagement with slot 292; the button is then rotated until cross-member 293 is in alignment with groove 291, wherein the cross-member is engaged upon release of button 169. In this position the top surface of the button is flush, or slightly below, the face of shelf 126 to 10 permit the inner target, of doubles, to ride across the shelf without hinderance.

The alignment and timing of the indexing mechanism to the target feeding and target throwing mechanism is accomplished when the trap is in the cocked position. With reference to FIGURE 13, when the trap is cocked, the arm of crank 9 is 30 below its center and to the right. At this position of the crank indexing gear 14 is rotated until the center lines of slots 16 are at about a 45 angle as shown in FIGURE 13. The indexing disc is then rotated until the center line of roller 12 is below a horizontal line through its center and to the right in about the same general direction as the arm of crank 9. At this position of the aforesaid elements, an indexing link chain 115 is mounted on and about sprockets 142 and 112 which are of equal diameter. As can be clearly seen, each complete revolution of shaft 8 drives indexing disc 15 through a complete revolution, however driving indexing gear 14 through only or one-fourth revolution.

It is pointed out that when the trap is in the cocked position roller 195 rides on the receding portion 281 of escapement cam 194. During the rotation of throwing arm 5, main shaft 8, and sprocket 142, link chain causes indexing disc 15 to rotate. During 270 degrees of angular movement from the cocked position of the trap the surface 20 of disc 15 slides within concave surface 18 of the Geneva indexing gear 14, however it is to be noted that after about 225 of angular travel, notch 28 of disc 15 just begins to come opposite index gear 14. After 270 degrees of angular travel drive roller 12 of index disc arm 109 begins its entry into a slot 16 of index gear 14. On continued angular travel drive roller 12 forces the slotted ends of gear 14 to rotate within the opening for said slots formed by the passage of notch 28 in rotation of disc 15. On completion of 360 angular path of roller 12, the indexing gear has been given a rotation of 90, again bringing a concave surface 18 of gear 14 into sliding engagement with surface 20 of disc 15 thereby locking gear 14 against further rotation. This 90 of rotation of gear 14 occurs for each complete revolution of disc 15, and accordingly for each complete revolution of main shaft 8.

This 90 of rotation of gear 14 is transmitted by appropriate gearing, described above, to impart, and accordingly index, an angular rotation of 36 to magazine 257 carrying ten stacks of targets. As noted above this is accomplished by use of a gear ratio of 2.5 to 1 in the selection of gears 215 and 226. Accordingly each complete revolution of main shaft 8, by the above described gear train, brings successive stacks of targets into register for delivery of targets to the feed shelf 126 and carrier 33.

Release of the targets from the bottom of the stacks in the rotary magazine to shelf 126 is controlled by the escapement mechanism which comprises essentially escapement assembly 235, rod 203, escapement levers 270 and 196, and escapement earn 194.

Escapernent lever 270 is mounted on escapement shaft 198 at about 90 to escapement drive 196 with respect to the point of contact of arm 199 with escapement rod 203 and to follower 195. When follower rides on receding portion 281 of escapement cam 194 escapement level 270 is in a retracted position. Follower 195 is held against receding portion 281 through the force submitted by the action of escapement spring 214 against rod 203 and in turn against arm 199. Since no force is exerted against arm 236 of escapement lever 235, the resilient escapement cushion 241 is held against the periphery of the bottom target by spring 271, against guides 230 with SlJfi'lClEIlt force to support a stack of targets above the bottom one. This bottom target and all the targets above it are thus secured against dropping. When follower 195 rides on the protuberant portion 280 of target escapement earn 194 a clockwise force is submitted through 198 and escapement lever 270 against escapement rod 203 and in turn against arm 236 of target escapement assembly 235. This applied force on arm 236 pivots escapement assembly 235 against the force of spring 271 to bring the resilient cushion out of contact with the bottom target in the stack thereby permitting it to drop upon the feed shelf 126 which supports the stack of targets during the period of time follower 195 rides on protuberant portion 280 of cam 194. As the receding portion 281 rotates opposite follower 195, cushion 241 closes on the second from bottom target, at a time prior to lowering of the feed shelf 126 to deliver the bottom target to carrier 33.

Mounted on base 145 is an angle changing motor 248 which submits by means of a flexible coupling 151 rotation to angle changing worm 152. Meshing with worm 152 is an angle changing worm gear 154 fixedly mounted by means of key 155 on the upper portion of a rotatable shaft 153. Fixedly mounted on lower end of shaft 153 by means of key 156 is angle changing pinion 157 which turns as a unit with worm gear 154. Mounted adjacent worm 152, worm gear 154, shaft 153 and pinion 157 are a series of lubricant wicks 479 which serve to carry lubricant to the worm gearing. Shaft 153 is rotatably mounted by means of appropriate bushings into the bottom of base 145 and into a cover plate 319 which is fixed by means of screws to the top of base 145. An angle changing idle gear 159 with hub 167 meshes with pinion 157 and is rotatably mounted about pin 158. A control hub gear 170 is rotatably mounted about a shaft 171 which in turn is mounted in the bottom of base 145. Gear 170 meshes with idle gear 159 and has eccentrically and fixedly mounted on it by means of pin 176 a hub 172. Hub 172 has formed on its upper portion a small shoulder to support an angle changing control gear 177 which is concentrically and rotatably mounted about the upper portion of the hub 172. Meshing with control gear 177 and concentrically mounted with drive gear 170 is an angle changing ring gear 179 which is fixedly mounted by means of pins 182 to an angle changing disc driver 181 which in turn is fixedly mounted by means of key 183 to shaft 171 and hub of angle changing disc 150. A cover plate 184 containing an opening for disc driver 181 is mounted by means of appropriate fasteners to the top of base 145. The top surface of cover plate 184 is substantially flush with the top surface of disc driver 181.

The angle changing disc 150 containing a plurality of holes 160 in its top surface at varied distances from its center is mounted on shaft 171 and is provided with a hub 320 which is rigidly attached by means of key 183 to the disc driver 181. Mounted in one of the holes 160 by means of spread adjusting screw 185 is one end of an angle changing link 148 connected at its other end by means of pin 192 to swivel base 143. The trap is forced to move through the desired are by the angle changing link 148 connected at one end to swivel base 143 and at its other end to the spread adjusting screw 185 mounted in one of the holes, in the instant embodiment one of six holes, in the angle changing disc 150. The spread or magnitude of oscillation is controlled by the crank radius of the particular hole in disc 150 in which spread adju'sting screw 185 is mounted.

In order to prevent the shooters from guessing the direction of succeeding target launchings the trap is oscillated over the prescribed arc in a repetitive non-uniform, non-rhythmic, non-cyclic manner by a hesitant progressively counter-clockwise rotation of the angle changing disc 150. This motion of disc 150 is obtained by the above described gearing through their functions which follows.

The angle changing motor 248 drives the control hub gear 170 at a constant counter-clockwise reduced speed through the means of an angle changing worm 152, angle changing worm gear 154, angle changing pinion 157 and angle changing idle gear 159. The angle changing control hub 172 is mounted eccentrically upon, and driven by, the control hub drive gear 170. The angle changing control gear 177 is journaled upon the eccentric portion of the control hub and constrained to a combined oscillatory and gyratory motion by the angle changing control link 178.which has an upstanding control link stud 180 engaging a hole in the rim of control gear 177 while its other end is pivotally anchored to hub 167 of idle gear 159. The control gear 177 is in constant mesh with the internal teeth of angle changing ring gear 179 which turns as a unit with, and drives, the angle changing disc driver 181 and the angle changing disc 150.

In the instant embodiment, control hub 172 is eccentrically formed about a concentric portion 321 about which is mounted control hub drive gear 170. Although this specific embodiment is illustrated it is obvious that hub portion 321 is not required. As noted above drive gear 170 may be rotatably mounted on shaft 171 and control hub 172 also rotatably mounted on shaft 171 and resting on drive gear 170 or the eccentric hub 172 may be formed integrally with the gear 170.

The conversion of the constant speed of rotation of the angle changing control hub 172 and its drive gear 170 to non-uniform rotation of the angle changing disc may be explained as follows:

First assume that, instead of attaching link 178 to gear 177 at point 180 in rim of gear 177, the attachment point 180 is moved to the end of an infinitely long arm rigidly attached to the gear 177. With such an arrangement the control gear would be constrained to gyrate, but not oscillate, as the drive gear and its eccentric hub 172 are rotated; the ring gear would be driven at a like constant velocity but at a reduced speed. As the imaginary arm on control gear 177 is made progressively shorter the gyratory motion of said control gear is modified by a superimposed oscillatory motion which in turn is transmitted proportionately to the ring gear 179 causing periodic acceleration, deceleration, hesitation and reversal in the rotary motion of the latter.

With the extremely short imaginary arm achieved by the connection of control link stud in the rim of gear 177 the magnitude of oscillation imparted to gear 177 is such that it rapidly advances or retards the output motion of ring gear 179 and angle changing disc 150 at various points in the cycle depending upon the ratio of gears and proportions of the links.

The ratios and proportions in the instant embodiment were chosen to provide a motion which in conjunction with the various rates of shooting ranging from slow to extra fast would result in a mixing of target discharge angles which would be difiicult for the shooters to predict. The specific selection of ratios and proportions will be hereinafter described together with FIGURE '16 illustrating the results of the above non-uniform motion.

In association with the electrical system which provides both power and control for the trap and which includes the motor 7, there is a release solenoid 87 having a plunger 86 for pushing firing pin 113 slidably carried in the firing pin guide 114 mounted in gear housing 3 to initiate the throwing operation. Solenoid 87 is mounted by suitable fasteners under a solenoid housing 146 provided for convenience with a hand grip 147; and housing 146 in turn is mounted by means of screws 448 and 149 to mainspring housing 4 so as to become in effect a part of frame 2.

The electrical wiring system of the trap may be described best with reference to FIGURE 15 wherein power is suplied to lines 300 and 301 by means of receptacle 298 and plug 299 from a power source 297 Power line 300 divides into lines 303 and 302 which latter is connected to the middle pole 304 of the switch unit 317 contained in switch assembly 305. Power line 301 is connected to the middle pole 308 of another switch unit 318 also contained in switch assembly 305 and the line 301 is also connected to one pole of switch 312. The

13 other side of switch 312 is connected with one side' of angling motor 248.

Switch unit 317 is a three pole unit containing poles 304, 306 and 307. The unit is so designed that it may be locked or set to stay in contact with pole 307 or in the neutral position, however, requiring a continued and applied pressure to maintain it against contact 306 which is-connected to line 313 which is connected to one side of solenoid 87 and to one pole of switch 311. Switch 3'18 is similarly constructed to function in like manner as unit 317. However, unit 318 has a shunt 315 shorting contacts 309 and 310. Contact 307 of unit 317, on the other hand, is unconnected to or from any source.

A line 314 connected at pole 310 leads and connects to the other side of solenoid 87 and into one side of trap motor 7. In practice, switch units 317 and 318 are so arranged that they are operated as a unit in closing poles 308 and 304 respectively against contacts 310 and 306.

Switch 312 may if desired be also contained in switch assembly 305 and various wires leading from assembly 305 may be contained in a single insulating cable extending from the switch assembly. Line 303 leads from its juncture with line 300 to the other side of angling motor 248, to the outer side of trap motor 7 and to the other side of switch 311. The operation of angling motor 248 is controlled by opening or closing switch 312. In operation poles 308 and 304 are switched into contact respectively with contacts 309 and 307. This position of the switch uni-ts completes the circuit to trap motor 7 which is set into operation. Contact 309 also connects one side of solenoid 87 to power line 301. The circuit to solenoid 87 is completed by closing switch 311. It is to be noted that the operation of self angling motor 248 is independent'of trap motor 7 and solenoid 87. Trap motor 7 and solenoid 87 are deactivated by opening switch units 317 and 318. These switch units provide a safety feature in that by momentarily switching poles 308 and 304 against contacts 310 and 306, solenoid 87 and motor 7 are momentarily activated to release the restraining means holding the throwing arm to release and discharge any target contained thereon, and to relieve the arm in the firing position upon release of the switch to return to neutral.

With the'trap in cocked position with a target emplaced upon the carrier arm plate 33 from the stack 316 in the magazine, the target is thrown by momentarily closing'the electric contacts of the release switch 311 (FIGUREIS), whereupon release solenoid 87 is energized and its plunger 86 pushes firing pin 113 against the end of firing bar 84 causing firing pawl shoulder or tooth 85 to engage with and be moved to the right by ratchet wheel 59 which is continuously turned counterclockwise (FIGURE 5). Thus moved, firing bar 84, acting through firing bar'stud 83, exerts a force on the end of operating arm or lever 82 of the sear member '80 which as a result is turned to lift the sear 79 out of notch 78 formed in therim 77 of control cam 65 (FIGURES 4, 5 and 6). This releases the control cam 65, main shaft8, target feed cam 31, throwing arm 5 and target escapement cam 194, through sprockets 1 42 and 112 and link chain 115, to turn counter-clockwise in unison leaving arm 5 free to throw the target from the carrier plate 33 under the impetusof tensioned mainspring 6 acting from a point at which mainspring crank stud 45 is about 30 following out dead center. During the first part of the target throwing or firing operation, the follower 97 of the cocking pawl 91 rides the protuber-ant portion 75 of cam 65 holding the cocking pawl tooth 96 from clattering along the teeth of'ratchet 74 of ring gear 73 which during firing also turns counter-clockwise in the same direction as arm 5, main shaft 8, and continuously turning sun gear 62 inasmuch as the. control cam 65 carrying the planetary gears 70, 71 and 72 is turning with main shaft 8 far more rapidly under the impetus of mainspring 6 than the rate at which the planetary gears 14 are cause-d to turn about planet gear studs 67, 68 and 69 under the impetus of the sun gear 62 driven by the motor 7.

At the beginning and for about the first 60 of the throwing operation target feed cam 31, acting through feed cam roll 128, target feed arm 127, and feed bracket or shelf operating operating roller 161, holds the target feed shelf 126 at the lower end of its travel at which shelf 126 is in line with the carrier plate 33 of rotating arm 5. At about 60 of the turning cycle of the arm measured from the cocked position, feed cam 31 begins to permit elevation of the feed shelf 126 which at about of rotation arrives at the top position which is slightly below the bottom target of the stack 116. When the arm 5 and cams 194 and 31 arrive at about the mark of angular travel, target escapement cam 194 causes the target escapement cushion 241 to begin opening. At the position the cushion is retracted and the escapement is fully open and permits the entire stack 316 to drop a slight distance of about of an inch to upraised feed shelf 126 thereby positioning the second from bottom target opposite the cushion 241. With the stack 316 thus supported, further rotation of cam 194 to about 245 permits the cushion 241 to grip the second from bottom target under the action of spring 271. After about 260 degrees of travel, feed shelf cam 31 lowers the shelf 126 carrying only a single target by about l /z-inches to a position in line with the carrier plate 33 where it is picked up and carried by the carrier plate 33, during about the last 20 of its angular travel to the cocked and ready-to-fire position. It is to be noted that the greatest target transfer movement is a movement of but a single supported target and not the entire stack. It is to be further noted that feed shelf 126 in coming up to take down a target from the stack stops just abit short of meeting with the stack so as not to bump it, which would be likely to break one or more of the frangible targets.

Before target feed shelf 126 is lowered from its elevated positions, at about the 240 mark of angular travel of the arm 5, the crank stud 45 has shot beyond its dead center by about 90 and begins to oscillate back or clockwise together with control cam 65. This sudden incipient movement of reversal causes planetary gears 70, 71 and 72 to tend to reverse ring gear 73 and drive it clockwise. But since reversal of ring gear 73 is prevented by the cocking pawl 91, inasmuch as at this position of the parts, follower 97 of the pawl has dropped opposite the receding portion 76 of control cam 65 and permits cocking pawl spring 98 to force tooth 96 of the pawl against ratchet 74 of gear 73, the only action of ring gear 73 is to exert a force on the cocking pawl 91 which causes a torque force on the hold back pawl 94 and brings about clockwise (FIG- URE 6) movement of pawl 94 so that it too engages with ratchet 74 of gear 73, which under these circumstances of the mechanism is secured in stationary position. With ring gear 73 thus held stationary, rotation of the sun gear 62 causes planetary gears 70, 71 and 72 to move their studs 67, 68 and 69 in the counterclockwise direction carrying control cam 65, main shaft 8 and the throwing arm 5 until mainspring crank stud 45 arrives at the out dead center at which position mainspring 6 is fully tensioned. However at about the out dead center position which corresponds to about30 of angular movement ibefore throwing arm 5 arrives at the cocked ready-to-fire position, the target carried by descending target feed shelf 126 is picked up by carrier plate 33 and moved along by frictional forces with plate 33. During the last 90 rotation of main sh'aft8 and of disc 15 with arm 109, the Geneva gear 14 is turned 90 to bring a new stack of targets 316 into position above the feed shelf 126. It is to be noted that with the escapement cushion 241 fully closed upon the lowermost target of those remaining in the stack 116, final descent of target feed shelf 126 has begun at about 

1. A TARGET TRAP COMPRISING A BASE, A TARGET THROWING MECHANISM PIVOTALLY MOUNTED ON SAID BASE WITH SAID MECHANISM HAVING A TARGET THROWING ARM MOUNTED THERETO, MEANS FOR CONSTANT AND CONTINUOUS OSCILLATION OF SAID MECHANISM IN A REPETITIVE CYCLE OF NON-UNIFORM MOITIONS DURING THE COCKING AND THROWING FUNCTIONS OF SAID TARGET THROWING ARM, AND A MOTOR FOR CONTINUOUSLY DRIVING SAID OSCILLATING MEANS, SAID OSCILLATING MEANS COMPRISING A DRIVING GEAR, A GEAR TRAIN CONNECTING SAID MOTOR AND DRIVING GEAR, A CYLINDRICAL HUB ECCENTRICALLY MOUNTED ON THE CENTER OF SAID DRIVING GEAR, AN EXTERNALY TOOTHED SECOND GEAR CONCENTRICALLY JOURNALED ABOUT SAID HUB, A LINK PIVOTALLY FIXED AT ONE END TO SAID SECOND GEAR AND PIVOTALLY FIXED AT ITS OTHER END AT A POINT REMOTE FROM SAID SECOND GEAR, AN INTERNALLY TOOTHED CIRCULAR THIRD GEAR MOUNTED IN AXIAL ALIGNMENT WITH SAID DRIVING GEAR AND MESHING SAID SECOND GEAR, AND MEANS TO TRANSMIT THE MOTION OF SAID THIRD GEAR TO SAID TARGET THROWING MECHANISM. 